Exhaust condensers



R. E. NELSON 2,966,233

EXHAUST CONDENSERS Filed April 24. 1959 Dec. 27, 1960 GASES OUT EXHAUST I8 GASES lN INVENTOR \REJECT WATER United States Patent ice EXHAUST CON DENSERS Robert E. Nelson, Willow Springs, Calif. (Willow Springs, Rosamond, Calif.)

Filed Apr. 24, 1959, Ser. No. 808,640

Claims. (Cl. 183-40) This invention relates to the condensation of water from the exhaust of an internal combustion engine for use in the engine cooling system. Reference is made to my United States Patent No, 2,591,187, in which the essential features of the installation and operation of engine exhaust condensers are explained.

Exhaust condensers have come into wide use in the past few years, particularly with natural-gas engines in oil-field pumping service. The greater proportion of these have been with multi-cylinder engines. Although the condenser shown and described in this application was developed primarily for use with'single-cylinder engines, it is also adaptable to multi-cylinder use.

Most internal combustion engine exhaust systems are subject to rapid periodic transients of pressure, both above and below atmospheric. These are sometimes employed to obtain a net forward flow of exhaust gases through the condenser by placing in series with the condenser at its outlet a sensitive pulse valve, which is adapted to pass gases during positive peaks of pressure but to restrict return flow during negative peaks. This is a particularly useful expedient where the average or static equivalent exhaust pressure is insutficient to supply the condenser without aid, and where the imposition of a restriction on the exhaust system to increase the available pressure is impracticable or undesirable.

A difliculty with such pulse valves, which have to operate over an extremely large number of cycles and are subject to impact between moving and stationary elements, has been wear and fatigue of the moving element, which is limited in useful life and requires periodic replacement. In this invention it is my purpose to extend greatly the life of the moving element of a pulse valve by limiting the amount of its motion in response to the exhaust-gas requirements of the condenser. This limitation I accomplish by employing the thermostatic element normally used to control the flow of gases through the condenser and using the moving element of the pulse valve to perform also the function of the flow-control valve normally a part of the condenser circuit.

Early attempts to accomplish the foregoing purpose resulted in the placement of the pulse valve in the normal flow-control position, which is between the first or purifying section and the second or main section of the condenser. An unwanted consequence of this placement was the exposure of the water reject line to the fluctuating pressures of the exhaust system, with resultant breathing through the reject line and dilution of the condenser gases with outside air, thereby reducing the usable water yield of the condenser, sometimes sharply. In the present invention 1 overcome this difiiculty' by separating the thermostat element and the pulse valve, placing the thermostatic element in a desired position to respond to the temperature of the gases passing from the first to the second condensing section but locating the pulse valve in the circuit ahead of the first condensing section and providing means for mechanically interconnecting these 2,966,233 Patented Dec. 27, 1960 elements. This solution has been outstandingly successful.

Another purpose of the present invention is to obtain a favorable rate of production of usable water from a relatively compact and inexpensive unit. This I have accomplished by taking advantage of the available pressure-drop past the pulse valve to obtain a high-velocity stream in the first condensing section and bringing this stream in immediate contact with the walls of the condensing chamber, and by employing an axial transfer from the first to the second chamber, which results in an effective semi-toroidal pattern of fiow in that chamber.

In the form illustrated, my invention satisfies its functional requirements with a simple and inexpensive arrangement of elements which is nevertheless durable and reliable in function.

In the drawing, the numeral 1 indicates generally the admission section. 2 is the first condensing or purifying section and 3 the second or main condensing section, 4 is the thermostat mounting cap. 5 is the gas exit section. Sections 1, 2, 3 and 4 are assembled co-axially by means of conventional cap screws, one of which is shown at 36. Section 5 is similarly mounted to section 3. The necessary gaskets between these named sections are shown at 12, 23, 34 and 54. Mounting of the condenser as a whole is usually vertical, and is accomplished by means of the pad 17 and mounting stud 11, in any suitable conventional manner.

Exhaust gases from the engine supply take-oft, which is conventional, enter the admission section 1 through the port 10. It is normally recommended that the exhaust take-off point be at a point in the system well separated from that of delivery to atmosphere, both to insure satisfactory intensity and duration of the pressure pulses and to prevent entry of outside air by back-flow from the atmospheric exit point. Gases entering the admission section at 10 pass into the space 15 formed by the annulus 13 and the center riser or boss 14. The space 15 is terminated against the thin pulse disc 46, which seats against the annulus 13 and the center boss 14. The post 19, pressed into the boss 14, centers the disc 46. The end-cup 45 of the thermostat assembly is initially spaced away from the disc 46 to allow the disc to move axially away' from the seat 13. Positive exhaust-pressure pulses cause the disc to lift from its seat and gases to pass into the first condensing chamber 20. Negative pulses return the disc to its seat and closure.

Gases entering the chamber 20 pass along the wall thereof until reversed by the skirt 21, around which they must pass to continue axially through the center annular barrier 37 into the main condensing chamber 38. These gases first pass over the thermostat element 40 and proceed until reversed in direction by the thermostat cap 4, after which they pass back along the wall of the chamber 38. They are finally collected laterally into the exit port 39, from which they pass to atmosphere through the elbow 5 and tube 51. 1

Usable condensate from the main condensing section 3 leaves through the port 30 to a conventional delivery tube which leads to the engine cooling system and accepts water as required by the engine. Surplus water rises until it can overflow the skimming barrier 37, after which it passes into the first condensing section, carrying with it any floating impurities which may be present,

The water so collected joins that produced in the first section in the annular space 16 and finally passes out through the reject port 18 to a conventional disposal tube of desired length.

The thermostat 40 is preferably of a well-known solidto-liquid state type commonly known as a Vernatherm, and is capable of developing substantially more force than will usually be required. The base end of this eleavenues 7.3 men: is secured to the thermostat cap4'at 41. Temperature sensing is in response to the fiow of gases entering the chamber 38 from the first section chamber 20, as well as "by contact transfer ofheat from the mounting cap 4, which is also subject to contact with the same "stream er entering gases.

The moving end of the thermostat 40 is secured to the rod 42 at 47. The rod 42'. passes axially into the chamber '29 and is drilled at 48 to receive the post'19, which locates its lower end while allowing axial freedom. Theendcup 45,'the axial position of which controls the degree or freedom of the disc 46, is mountedyieldably on the rod 42 by means of the spring 44, bearing 'against the cup 45 and the ring 43 secured to the rod 42. Splitrin'g -"segments 49provideend location in normal'operation. Should the thermostat over-travel after completely closing the disc 46 against its seat, the spring 44 yields to prevent damage to the thermostat.

It will be seen that the pulse disc 46 is given -a substantial amount offreedom to travel in warming up and under'marginal conditions of exhaust gas supply. However,'as the condenser warms up the thermostat moves the cup '45 closer to the "pulse disc until the travel of the disc is just enough to maintain the gas flow needed tohold operating temperature. Thus the travel and attendant wear on the disc is minimized. It will also be evident that the first condensing section'and its reject port 18 are largely isolated from the exhaust-system pressure peaks by the interposition 'of the disc 46, since, when thesepeaks are large, thedisc will necessarily operate in a nearly closed.position and therefore eife'cti've'ly throtties the effect of the peaks.

I claim: v

1. In a ivater condenser, "admission means adapted to receive gases at pulsating pressurefrom the exhaust system of an internal combustion engine, exit means from said condenser for delivering spent gases to atmosphere, a pulse valve between said admission and said exit means and adapted to pass gases under positive exhaust system :pressure pulses but to restrict flow during negative pulses, said pulse valve having a moving element, a seat closure and a movable abutment for limiting the degree of opening of said moving element, a thermostatic element adapted to respond to variations in the operating'tem- :perature of said condenser, and means connecting said thermostatic element and said abutment, whereby said abutment may be moved in a direction to reduce the degree of possible opening of said moving pulse 'valve element as'the operating temperature of said condenser increases.

-2. Ina water condenser, admission means adapted to --receive gases at pulsating pressure from the exhaust system of an internal combustion engine, a condensing chamber, a pulse valve between said admission means and said condensing chamber and adapted to pass gases under positive exhaust system pressure pulses but to 'restrict flow during negative pulses, said pulse valve having a moving element, a-seat closure and a movable abutment for limiting the degree of opening ofsaid'moving element, a thermostatic element adapted to respond to variations in the operating temperature of said condenser,'and-means con'necting'said thermostatic element and said abutment, whereby said abutment may be-moved in a direction to "reduce the degree of possible opening "of said-moving .pulse valve' element as'the operating temperature of saidcondenser increases.

3. In a water condenser,'admission meansadaptedto receive gases at pulsating pressure from the exhaust sys tem of an internal combustion engine, a first condensing chamber, a second condensing chamberadapted to receive gases from the first, a pulse valve between said admission means and said first condensing chamber, said pulse valve being adapted'to pass gases under positive exhaust system pressure pulses but to restrict flow during negative pulses, said pulse valve having'a moving element, a seat closure and a movable abutment for limiting the degree of opening of said moving element, a thermostatic element adapted torespond to variations in the operating temperature of said condenser, and means connecting said thermostatic element and said abutment, whereby said abutment may be moved in a direction to reduce the degree of possible opening of said moving pulse valve element as the operating temperature of said condenser increases.

in the temperature of the fiowinggases passing'from said first condensing chamber to said second condensing chamber, andmeans connecting said thermostatic element and said abutment, wherebysaid abutment may be moved in a'direction to reduce the degree of possible opening of said moving pulse valve element as the operating temperature of said condenser increases.

5. In a Water condenser, admission means adapted to receive gases at pulsating pressure from the exhaust system of an internal combustion engine, a valve adapted to pass gases under positive exhaust system pressure impulses but to restrict flow during negative impulses, a first condensing section adapted to receive the delivery of said valve, a second condensing section adapted to receive gases from said first condensing section, a thermostatic element in said second condensing section and adapted to respond to the temperature variations of gases entering said second section, and a rod operably connecting with said thermostatic element and passing into said first condensing section to a point adjacent to said valve, said rod being adapted to limit by its motion from said thermostatic element the potential degree of movement of said "valve.

References Cited in the file of this patent UNITED STATES PATENTS 342,962 Hill June 1, 1886 963,463 Mueller' July 5, 1910 1,820,795 Gordon .et .al. Aug.'25, "1931 2,057,667 Blome Oct. 20, 1936 12324 Great Britain May 22, 1911 

